EP0557918B1 - Joint pour moteur à combustion interne - Google Patents

Joint pour moteur à combustion interne Download PDF

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Publication number
EP0557918B1
EP0557918B1 EP93102729A EP93102729A EP0557918B1 EP 0557918 B1 EP0557918 B1 EP 0557918B1 EP 93102729 A EP93102729 A EP 93102729A EP 93102729 A EP93102729 A EP 93102729A EP 0557918 B1 EP0557918 B1 EP 0557918B1
Authority
EP
European Patent Office
Prior art keywords
flat gasket
gasket according
combustion chamber
ring
support plate
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP93102729A
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German (de)
English (en)
Other versions
EP0557918A1 (fr
Inventor
Gerhard Walter
Erich Amann
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Elring Dichtungswerke GmbH
Original Assignee
ElringKlinger AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by ElringKlinger AG filed Critical ElringKlinger AG
Publication of EP0557918A1 publication Critical patent/EP0557918A1/fr
Application granted granted Critical
Publication of EP0557918B1 publication Critical patent/EP0557918B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F11/00—Arrangements of sealings in combustion engines 
    • F02F11/002—Arrangements of sealings in combustion engines  involving cylinder heads
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/02—Sealings between relatively-stationary surfaces
    • F16J15/06—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces
    • F16J15/10—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces with non-metallic packing
    • F16J15/12—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces with non-metallic packing with metal reinforcement or covering
    • F16J15/121—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces with non-metallic packing with metal reinforcement or covering with metal reinforcement
    • F16J15/122—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces with non-metallic packing with metal reinforcement or covering with metal reinforcement generally parallel to the surfaces
    • F16J15/123—Details relating to the edges of the packing

Definitions

  • the invention relates to a flat gasket for internal combustion engines for mounting between opposing surfaces of an engine block and a cylinder head with a carrier plate, which comprises openings aligned with the combustion chambers of the engine block and openings for the passage of coolant and lubricant flows, with combustion chamber surrounds and various sealing elements thereof Elastomer material, which have the latter sections, which separate the coolant flows and the lubricant flows from one another and surround them in a sealing manner, and with a support for limiting the compression of the sealing elements made of elastomer material, which defines the distance between the opposing surfaces of the engine block and cylinder head, the carrier plate essentially exclusively as a holder for the individual components of the flat gasket in the gasket plane in a section specified for assembly is formed from each other.
  • Such flat gaskets are known from FR-A 23 19 824, in which the combustion chamber surrounds and screw through holes are bordered with metal eyelets, which are incompressible and support the cylinder head on the engine block and thus prevent excessive compression of the elastomer sealing elements.
  • the thickness of the elastomer sealing elements be 15 to 30% larger than that of the support.
  • the object of the invention is to propose a flat gasket which, in principle having the same structure, can easily be adapted to different requirements on the part of the internal combustion engines to be fitted and which, in particular, also solves the problems with the particularly high demands on the cylinder head gasket engine designs.
  • This new concept of the construction of a flat gasket means that the carrier plate no longer performs a sealing function, as was previously the case, but only functions as an assembly aid, which ensures that the individual components of the flat gasket, namely in particular the combustion chamber surrounds and the sealing elements, the enclose the cooling water flows and lubricant flows and seal them from each other and towards the combustion chamber so that they are in the correct position between the engine block and the cylinder head.
  • combustion chamber surrounds or sealing elements can then be combined with the carrier plate, so that one can meet a multitude of different requirements with the same type of flat seal.
  • the elastomer materials can also be adapted - especially for coolant or lubricant breakthroughs.
  • the combustion chamber surrounds preferably comprise a metallic surround ring which delimits the combustion chamber from the rest of the seal and seals it off.
  • the metallic ring can be made of solid material, for example, and then carries a circumferential groove on its top or bottom.
  • the circumferential groove gives the solid ring a certain degree of flexibility, so that the ring can deform somewhat during assembly and can compensate for tolerances on the surfaces of the engine block and cylinder head.
  • the ring can have a U-shaped profile that is open on the side facing away from the combustion chamber, wherein resilient metallic material is preferably used for this purpose in the manufacture of the bezel ring.
  • the metallic ring with one of the legs of the U-shaped profile is connected to the carrier plate via a bent part.
  • the metallic ring can in particular be formed in one piece with the carrier plate, i.e. the openings in the area of the combustion chamber are kept somewhat smaller during the manufacture of the carrier plate, in which case, in a further process step, the edge of the carrier plate facing the interior of the combustion chamber is flanged and thus forms the metallic bezel ring with the U-shaped profile. It may be necessary to bend the carrier plate at the transition to the bezel to arrange the bezel symmetrically to the carrier plate level.
  • the combustion chamber surround can include a radially outwardly projecting edge region, which is optionally formed in one piece as a continuation of a leg of the U-shaped profile.
  • These expanded, outwardly projecting edge areas of the combustion chamber surround serve to overlap with areas of the cylinder head that are subject to particularly high loads, such as the cover of a swirl chamber in the case of diesel engines in the cylinder head.
  • the insert ring can comprise tabs projecting outwards, which can then be used to fasten the combustion chamber surround to the carrier plate.
  • the insert ring in the bezel ring can also be sandwiched by metallic layers.
  • the U-shaped profile of the bezel is essentially completely filled with the soft material sealing material.
  • the U-shaped profile is at least partially filled with a graphite filling, in particular expanded graphite.
  • the graphite filling can be in the form of a ring, for example with a circular cross section and arranged adjacent to the closed end of the U-shaped profile.
  • the elastomer sealing elements it is possible not to apply the elastomer sealing elements to the carrier plate, but rather to spray them on at the edge thereof, so that they optionally encompass a marginal area of the carrier plate to a small extent.
  • the injection molding of the elastomer sealing elements on the carrier plate is possible because no large holding forces are necessary, since the carrier plate, as already mentioned, yes in the essentially only has the function of an assembly aid and is essentially without function in this regard during the further life of the cylinder head gasket in the installed state.
  • the same also applies to the mounting of the combustion chamber surrounds, since these remain firmly in place in the installed state and no longer require fixation by the support plate.
  • the elastomer sealing elements preferably have the shape of a double rib, with which a particularly efficient and secure sealing of the individual areas from one another can be ensured.
  • the screw forces can essentially be provided for pressing the combustion chamber surround, where they are also required for a corresponding gas tightness, and it is sufficient for a tight seal of the coolant and lubricant flows to deform the elastomer sealing elements in order to achieve a continuous one
  • the support elements of the support define a distance such that it essentially specifies the thickness of the combustion chamber surrounds in the ideally compressed state and at the same time is somewhat less than the thickness of the flat seal on the areas to which elastomer sealing elements are applied.
  • the support elements can be made of flat material and attached as separate parts to the top and bottom of the carrier plate.
  • the carrier plate material is folded back onto itself one or more times in peripheral regions and is connected to the carrier plate itself via a cranked region.
  • Another alternative for the formation of the support elements is to manufacture them from sheet metal bent into U-profiles and to place them on the peripheral edge of the carrier plate.
  • the clamping effect of the U-profile sheets is often sufficient, and further fastening measures can be omitted.
  • the support elements it should preferably be ensured that these are arranged outside the areas of the carrier plate which are in contact with coolant and / or lubricant.
  • the combustion chamber surround and support elements can be formed in one piece. With a punching process, the combustion chamber surrounds and the support elements are then obtained as one component. Advantages are achieved in particular during assembly because, if necessary, all combustion chamber surrounds can be handled as one component together with the support elements.
  • Fig. 1 shows a partial view of a flat gasket provided with the reference numeral 10 for internal combustion engines, hereinafter referred to as cylinder head gasket, which is mounted between two opposite surfaces of an engine block and a cylinder head.
  • the cylinder head gasket 10 comprises a carrier plate 12 which is essentially matched to the outer contours of the engine block to be fitted.
  • the carrier plate 12 comprises a plurality of openings for the combustion chambers 14, 15, the passage of oil 16 or cooling water 18. Furthermore, the carrier plate 12 in the form of double or simple sealing lips, elastomeric sealing elements 20 are applied, here sprayed on, which extend essentially all around and adjacent to the peripheral edge of the carrier plate 12 and furthermore have sections which separate oil and coolant flows from one another. In the present case, it is provided that all oil-carrying streams are surrounded or surrounded in a sealing manner by elastomeric sealing lips 20. The coolant flows are sealed to the outside by parts of the sealing lips 20, while the sealing with respect to the combustion chambers 14, 15 is taken over by combustion chamber surrounds 22, 24.
  • combustion chambers 14 and 15 are surrounded by combustion chamber surrounds 22, 24, which in the present case are formed in one piece with the carrier plate 12, which is made here from a metal sheet.
  • the combustion chamber surrounds have on one side a tab 19 pointing away from the combustion chamber, which covers a swirl chamber insert fitted in the cylinder head on the cylinder head side.
  • the reference numerals 17 denote screw through holes. A more detailed description of the combustion chamber surrounds and the elastomer sealing elements is given below in connection with the description of FIGS. 3 to 7 and 8 to 14.
  • support elements in the form of U-shaped bent sheets 26 are placed on the outer edge of the cylinder head gasket according to the invention, which are held by the clamping action of the U-profile on the carrier plate and a partial embossing (not shown).
  • FIG. 2 shows a further cylinder head gasket 30 according to the invention with a metallic carrier plate 31, made from an unperforated sheet.
  • a metallic carrier plate 31 made from an unperforated sheet.
  • combustion chamber surrounds 32, 34 are fastened via tabs 36 which project radially from the combustion chamber surrounds 32, 34 and which are glued or spot welded to the carrier plate 31, for example.
  • the combustion chamber surrounds 32, 34 are inserted into cutouts 37, 38 of the carrier plate 31, which have a larger diameter than the combustion chamber surrounds 32, 34 themselves.
  • This example shows the sole support function of the carrier plate for the individual elements of the cylinder head gasket, such as the combustion chamber surrounds.
  • the carrier plate 31 also has openings for coolant flows 40 and lubricant passages 42 (only one shown).
  • the openings 40 also serve to calibrate the coolant flows.
  • cooling water flow does not require a special seal. Rather, it is sealed off from the combustion chambers by the combustion chamber surrounds 22, 24 or 32, 34.
  • the flat gasket according to the invention shown in FIG. 2 like the embodiment shown in FIG. 1, has support elements 48 attached to the peripheral edge of the carrier plate 31, which are made of sheet metal bent into U-shaped profiles. These support elements 48 are each arranged adjacent to screw through holes 50 and, adjacent to these force introduction points, define the distance to be maintained between the surface of the engine block and the opposite surface of the cylinder head, which ensures ideal compression of the combustion chamber surrounds 32, 34.
  • FIG. 3 shows a further embodiment of the flat gasket according to the invention with a carrier plate 120, combustion chamber surrounds 122, 124, elastomer sealing elements 126, 127 and support elements 128, 130.
  • the special feature of this embodiment lies in the integral design of the combustion chamber surrounds 122, 124 with the support elements 128 , 130.
  • the support elements 128 and 130 are held on the combustion chamber surrounds via a web 132, 134 and can be assembled together with them in one work step.
  • the inner edges of the combustion chamber surrounds are flanged and the parts of the support elements which protrude beyond the carrier plate 120 (not visible in FIG. 3) are folded around the edge of the carrier plate.
  • known soft material sealing material is arranged in the interior of the U-shaped profile, which counteracts a loss of setting of the combustion chamber surround during the life of the cylinder head gasket.
  • FIG. 5 shows an alternative embodiment for a metal ring in the form of a solid ring 56 which has a circumferential groove 58 on one side.
  • recesses 60, 61 running all around are provided on the inner and outer edge of the ring 54, which recesses weaken the solid material cause the ring 54 such that it has sufficient flexibility when pressed in the assembled state of the cylinder head gasket to adapt sufficiently to the respective surfaces of the cylinder head and engine block.
  • the ring 54 can be fastened to the carrier plate 12 by means of tabs or the like (not shown) to be molded on, or can simply be held in a press fit in a recess in the plate 12. It is only important that the combustion chamber surround, here the ring 54, be given good centering for the combustion chamber 15 for assembly and are securely fixed in the carrier plate 12 when handling the cylinder head gaskets.
  • FIG. 6 shows a further possible variant of a combustion chamber surround 64, a metal ring 66 with a U-shaped profile closed towards the inner radius receiving an insert ring 67 made of flat material.
  • a sandwich-like structure of five ring layers is thus formed, the ring 67 with a U-shaped cross section holding between the legs an area of the carrier plate 69 provided with a circumferential bead 70.
  • the carrier plate 69 is here advantageously made of spring steel, so that the combustion chamber surround has a sufficient springback effect during the operation of the engine and the load on the cylinder head gasket.
  • combustion chamber surrounds in the cylinder head gaskets according to the invention are not limited to the aforementioned examples, but rather show that the combustion chamber surrounds can be optimally adapted to any conceivable requirement, regardless of the other design of the cylinder head gasket.
  • FIG. 10 shows a further sectional view through a sealing element made of elastomeric material, a simple sealing lip being sufficient in this exemplary embodiment.
  • FIG. 11 shows a special case of a sealing element 88 which forms a sealing edge on one side towards a passage 90, while it is injection molded onto a support element 92 on the side opposite the passage 90.
  • Fig. 12 finally shows a sectional view through a sealing element 94, which is essentially the structure of the 9 corresponds to the sealing element, in which case the sealing element is also sprayed onto a carrier plate 96.
  • the peripheral part of the carrier plate 96 carries a support element 98, which consists of parts arranged on the top and bottom of the carrier plate 96 and made of a flat material.
  • FIG. 14 Another alternative is shown in FIG. 14, in which, similarly to FIG. 11, a support element 102 is held on a carrier plate 106 via a sealing element 104.
  • the contact area between the sealing element 104 and the support element 102 is sufficient for a secure mounting of the support element 102, while the end face of the carrier plate 106 would only offer insufficient support for this. Therefore, the sealing element 104 engages around the peripheral edge of the carrier plate 106 to a small extent.
  • FIG. 17 shows a flat gasket with a flat carrier plate 138 which extends from the edge 146 of the gasket to the combustion chamber.
  • a sheet metal layer 142 is placed on the support plate 138 over a large area, which likewise extends from the edge 146 of the seal to the combustion chamber, where the sheet layer 142 is flanged over the support plate 138 and forms a combustion chamber surround 140.
  • a support plate 144 is arranged on the side of the carrier plate 138 opposite the plate layer 142, which has a somewhat smaller thickness, the difference in thickness is, for example, 0.1 mm and, together with the carrier plate 138 and the plate layer 142, the distance from Engine block and cylinder head defined in the support area.
  • the thickness of the sheet metal layer 142 is typically approximately 0.5 mm and that of the carrier plate 138 approximately 0.4 mm.
  • the thickness of the support plate 144 is then also about 0.4 mm given the difference in thickness.
  • combustion chamber surround 140 shown in this example is not for all engines, but for the less critical, can be used with good success. If the combustion chamber surround has to withstand higher gas pressures, the combustion chamber surround 140 can be improved by providing the area of the carrier plate 138 covered by the combustion chamber surround 140 with a circumferential bead (not shown, but see, for example, FIG. 16).
  • the flat gasket 148 according to the invention shown in FIG. 18 comprises, in addition to a carrier plate 150, a sheet-metal layer 152 and a large-area support plate 154 which is arranged on the side of the carrier plate 150 opposite the sheet-metal layer 152.
  • a combustion chamber surround 160 is formed by flanging the sheet metal layer 152 around the carrier plate 150 crimped in the combustion chamber area. Due to the greater thickness of the sheet metal layer 152 compared to the support plate 154, there is a higher pressure on the combustion chamber surround.
  • the support plate extends in the area of the swirl chamber from the edge 162 of the seal to close to the flanged part of the sheet layer 152.
  • a partial area 164 of the support plate 154, which overlaps with the swirl chamber 158, is provided with two semi-beads, which support the swirl chamber 158 on the engine block (not shown) in an area away from the edge of the combustion chamber.
  • This additional support for the swirl chamber 158 fixes it particularly well in the cylinder head 156 in a defined position, in particular also in the case of thermal alternating loads.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Gasket Seals (AREA)

Claims (26)

  1. Joint plat (10) pour des moteurs à combustion interne pour le montage entre des surfaces opposées d'un bloc moteur et d'une culasse de cylindre, comportant un plateau de support (12) qui comporte des traversées (14, 15) dirigées vers les chambres de combustion du bloc moteur, ainsi que des traversées (16, 17) pour le passage de courants de réfrigérants et de lubrifiants, présentant des encadrements (22, 24) des chambres de combustion et des éléments d'étanchement (20) en matière élastomère et différents de ces encadrements, qui présentent des tronçons qui séparent les courants de réfrigérant et les courants de lubrifiant les uns des autres et qui les entourent de façon étanche, et présentant un appui (26) pour limiter la compression des éléments d'étanchement (20) en matière élastomère, qui définit la distance entre les surfaces opposées du bloc moteur et de la culasse de cylindre, le plateau de support (12) étant réalisé sensiblement exclusivement sous forme d'une monture pour les composants individuels du joint plat dans le plan d'étanchement à une distance les uns des autres qui est prédéterminée pour le montage, et les encadrements (22, 24) des chambres de combustion peuvent être pressés, et l'appui comporte des éléments d'appui (26) qui définissent la distance entre les surfaces opposées du bloc moteur et de la culasse de telle sorte que la distance détermine sensiblement l'épaisseur des encadrements (22, 24) des chambres de combustion à l'état pressé de façon idéale et est simultanément légèrement inférieure à l'épaisseur du joint plat dans les régions sollicitées par les éléments d'étanchement (20) en élastomère.
  2. Joint plat selon la revendication 1, caractérisé en ce que les encadrements (54) des chambres de combustion comportent un anneau d'encadrement métallique (56).
  3. Joint plat selon la revendication 2, caractérisé en ce que l'anneau métallique (56) est fabriqué en un matériau massif et comporte sur sa face supérieure ou inférieure une gorge périphérique (58).
  4. Joint plat selon la revendication 2, caractérisé en ce que l'anneau métallique (52) présente un profil en forme de U ouvert sur le côté détourné de la chambre de combustion (15).
  5. Joint plat selon la revendication 4, caractérisé en ce que l'anneau métallique (52) est relié par l'un des bras du profil en forme de U au plateau de support (12) via une partie coudée (54).
  6. Joint plat selon l'une ou l'autre des revendications 4 et 5, caractérisé en ce que l'anneau métallique (52) est réalisé en une seule pièce avec le plateau de support (12).
  7. Joint plat selon l'une quelconque des revendications 2 à 5, caractérisé en ce que l'anneau est relié au moyen de pattes faisant radialement saillie et en chevauchement avec le plateau de support.
  8. Joint plat selon l'une quelconque des revendications 1 à 7, caractérisé en ce que l'encadrement (24) de la chambre de combustion comporte une région de bordure (54) faisant saillie radialement vers l'extérieur, qui est en option réalisée en une seule pièce comme prolongement d'un bras du profil en forme de U.
  9. Joint plat selon l'une quelconque des revendications 4 à 8, caractérisé en ce que le profil en forme de U de l'anneau (52) est rempli avec une masse d'étanchement en matière molle.
  10. Joint plat selon l'une quelconque des revendications 4 à 9, caractérisé en ce que l'encadrement (72) de la chambre de combustion comporte un insert métallique annulaire (80), constitué en option en un matériau plat perforé, qui s'étend concentriquement par rapport à l'anneau d'encadrement et qui est agencé entre les bras du profil (74) en forme de U.
  11. Joint plat selon la revendication 10, caractérisé en ce que l'insert annulaire (69) présente une moulure périphérique (70) sur sa partie qui chevauche l'anneau d'encadrement (66).
  12. Joint plat selon l'une ou l'autre des revendications 10 et 11, caractérisé en ce que l'insert métallique annulaire (86) est noyé dans un matériau d'étanchement en matière molle (84) du moins dans la région du chevauchement avec le profil en forme de U (82) de l'anneau d'encadrement.
  13. Joint plat selon l'une ou l'autre des revendications 9 et 12, caractérisé en ce que le profil en forme de U (82) est rempli sensiblement entièrement avec le matériau en matière molle (84).
  14. Joint plat selon l'une quelconque des revendications 4 à 12, caractérisé en ce que le profil (74) en forme de U est rempli du moins partiellement avec une couche de fil ou de cordon métallique (76) ou avec un remplissage de graphite (76), en particulier un graphite expansé.
  15. Joint plat selon la revendication 14, caractérisé en ce que le remplissage de graphite (76) présente une forme annulaire et est agencé au voisinage de l'extrémité fermée du profil (74) en forme de U.
  16. Joint plat selon l'une quelconque des revendications précédentes, caractérisé en ce que les éléments d'étanchement (20) en élastomère sont appliqués sous forme de nervure sur la face supérieure et inférieure du plateau de support (12), et en ce qu'ils sont en particulier projetés ou collés, et en option reliés les uns aux autres via des trous de perforation (116) dans le plateau de support.
  17. Joint plat selon l'une quelconque des revendications 1 à 15, caractérisé en ce que les éléments d'étanchement (104) en élastomère sont projetés sur le plateau de support (106), et entourent en option une région de bordure du plateau de support (106).
  18. Joint plat selon l'une ou l'autre des revendications 16 et 17, caractérisé en ce que les éléments d'étanchement en élastomère (20) présentent la forme d'une nervure double.
  19. Joint plat selon l'une quelconque des revendications précédentes, caractérisé en ce que les éléments d'appui (98) sont fabriqués en un matériau plat et fixés en tant que pièces séparées sur la face supérieure et inférieure du plateau de support.
  20. Joint plat selon l'une quelconque des revendications 1 à 18, caractérisé en ce que les éléments d'appui (108) sont formés par des parties périphériques du plateau de support (112), qui sont repliées sur elles-mêmes une ou plusieurs fois.
  21. Joint plat selon l'une quelconque des revendications 1 à 18, caractérisé en ce que les éléments d'appui (100) sont formés par des tôles à profil en U et sont enfichés, et en option additionnellement fixés, sur la bordure périphérique du plateau de support (96).
  22. Joint plat selon l'une quelconque des revendications 1 à 18, caractérisé en ce que les éléments d'appui (102) sont réalisés sous forme de pièces massives parallélépipédiques et retenus sur la bordure du plateau de support via des ponts en élastomère (104), lesquels peuvent en option simultanément être des éléments d'étanchement.
  23. Joint plat selon l'une quelconque des revendications précédentes, caractérisé en ce que les éléments d'appui (26) sont agencés sur le plateau de support (12) à l'extérieur des régions qui sont en contact avec le réfrigérant et/ou le lubrifiant.
  24. Joint plat selon l'une quelconque des revendications précédentes, caractérisé en ce que l'appui (142) est réalisé en une seule pièce avec l'encadrement (140) de la chambre de combustion.
  25. Joint plat selon l'une quelconque des revendications 1 à 24, caractérisé en ce que le plateau de support (12) est réalisé en une seule pièce avec un ou plusieurs éléments d'étanchement (52).
  26. Joint plat selon l'une quelconque des revendications 1 à 25, caractérisé en ce que l'épaisseur de toutes les couches est supérieure au niveau de la bordure (160) de la chambre de combustion à celle dans la région de l'appui.
EP93102729A 1992-02-26 1993-02-20 Joint pour moteur à combustion interne Expired - Lifetime EP0557918B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4205824A DE4205824A1 (de) 1992-02-26 1992-02-26 Flachdichtung fuer verbrennungskraftmaschinen
DE4205824 1992-02-26

Publications (2)

Publication Number Publication Date
EP0557918A1 EP0557918A1 (fr) 1993-09-01
EP0557918B1 true EP0557918B1 (fr) 1996-07-03

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EP93102729A Expired - Lifetime EP0557918B1 (fr) 1992-02-26 1993-02-20 Joint pour moteur à combustion interne

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EP (1) EP0557918B1 (fr)
DE (2) DE4205824A1 (fr)
ES (1) ES2089606T3 (fr)

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DE4308820C2 (de) * 1993-03-19 1999-06-02 Elringklinger Gmbh Mehrlagenmetalldichtung für Verbrennungskraftmaschinen
FR2724439B1 (fr) * 1994-09-13 1996-10-25 Curty Payen Sa Joint metal-elastomere, notamment joint d'etancheite plat
US5951021A (en) * 1994-11-22 1999-09-14 Japan Metal Gasket Co., Ltd. Metallic gasket
GB2301636B (en) * 1995-06-02 1998-12-16 Coopers Payen Limited Manufacture of gaskets
JP3460819B2 (ja) * 2000-11-09 2003-10-27 石川ガスケット株式会社 ヘッドガスケット
DE10060555B4 (de) * 2000-12-06 2006-11-23 Carl Freudenberg Kg Flachdichtung für eine Kolbenkraft- oder Arbeitsmaschine
DE10060514B4 (de) 2000-12-06 2006-11-30 Carl Freudenberg Kg Flachdichtung für eine Kolbenkraft- oder Arbeitsmaschine
DE102008030787A1 (de) 2008-06-28 2009-12-31 Elringklinger Ag Zylinderkopfdichtung
DE102012101384A1 (de) * 2012-02-21 2013-08-22 Elringklinger Ag Flachdichtung, insbesondere Zylinderkopfdichtung

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DE1750805C2 (de) * 1968-06-06 1974-08-01 Reinz-Dichtungs-Gesellschaft Mbh, 7910 Neu-Ulm Vorlagering für Weichstoff-Flachdichtungen
GB1517539A (en) * 1975-07-30 1978-07-12 Engineering Components Ltd Gaskets
DE2818472A1 (de) * 1978-04-27 1979-10-31 Goetze Ag Metallische zylingerkopfdichtung
US4213620A (en) * 1978-12-20 1980-07-22 General Motors Corporation Cylinder head gasket
FR2446970A1 (fr) * 1979-01-18 1980-08-14 Renault Vehicules Ind Joint de culasse perfectionne pour les moteurs a combustion interne
GB2159215A (en) * 1984-05-22 1985-11-27 Corrugated Packing Sheet Metal Cylinder head gaskets
DE3509136A1 (de) * 1985-03-14 1986-09-18 Elring Dichtungswerke Gmbh, 7012 Fellbach Zylinderkopfdichtung
DE3720838A1 (de) * 1987-06-24 1989-01-05 Lechler Elring Dichtungswerke Flachdichtung, insbesondere zylinderkopfdichtung
US4796897A (en) * 1987-08-28 1989-01-10 Fel-Pro Incorporated Head gasket with beam-functioning fire ring
FR2621352B1 (fr) * 1987-10-02 1990-02-09 Curty Soc Joint de culasse pour moteur a combustion interne
FR2645934B1 (fr) * 1989-04-18 1991-07-05 Curty Soc Procede de fabrication d'un joint comportant un corps metallique equipe d'au moins un element d'etancheite souple

Also Published As

Publication number Publication date
DE4205824A1 (de) 1993-09-02
EP0557918A1 (fr) 1993-09-01
DE59303098D1 (de) 1996-08-08
ES2089606T3 (es) 1996-10-01

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